Typographical composing machine



Nov. 2, 1937. R MEAD 2,097,732

TYPOGRAPHICAL CQMPOSING MACHINE Filed Jan. '15, 1936 3 Sheets-Sheet 1 QN I QR N mi: Qksi 2 INVENTOR A TTORNEI Z Nov. 2, 1937. R. R'MEAD2,097,732

TYPOGRAPHICAL COMPOSING MACHINE Filed Jan. 15, 1936 5 Sheets-Sheet 2Nov. 2, 1937. I RRMEAD 2,097,732

TYPOGRAPHICAL COMPOS ING MP CHINE Filed Jan. 15, 1936 5 Sheets-Sheet 3 I11v VENTOR M A TTORNE 1 .5

Patented Nov. 2, 1937 UNITE. STATES PATENT OFFECE Richard R. Mead,Queens Village, N. Y., assignor to Mergenthaler Linotype Company, avcorporation of New York Application January 15, 1936, Serial No. 59,207

22 Claims.

This invention relates to typographical composing machines, such asLinotype machines of the general organization represented in LettersPatent of the United States to O. Mergenthaler No. 436,532, whereincirculating matrices are released irom a magazine in the order in whichtheir characters are to appear in print and then assembled in line, thecomposed line transferred to the face of a slotted mold, the mold filledwith molten metal to form a slug or linotype against the matrices whichproduce the type characters thereon, and the matrices thereafterreturned through distributing mechanism to the magazine from which theystarted.

More particularly, the invention relates to machines of this characteremploying matrices of widely varying sizes. Heretofore, it has been thecustom to operate the assembler or conveyor belt at but one speed, whichspeed is designed to allow the matrices to be composed in the assemblerelevator at a rate (normally about six lines per minute) consistent withthe speed of operation of the casting and distributing mechanisms.

This rate of composition, although not the fastest at which the machinemay operate if only the smaller or thinner matrices are used, hasnevertheless been found to be a good average and has given satisfactoryresults. The present trend, however, is toward machines with widermagazines capable of handling full matrix fonts up to 36 pt. size, buthere a serious difficulty arises, since it is apparent that a normalrate of speed of composition (which for the smaller matrices would beequivalent to, say, six lines per minute) would for the larger matrices,due to their greater thickness, be equivalent to perhaps eight or ninelines per minute, a speed at which the distributing mechanism can notproperly handle matrices of such larger sizes. Then, too, when thelarger matrices are delivered at such high rates of speed to theassembler, the pounding of the matrices against each other, due to theirgreater weight, results in their rapid destruction.

According to the present improvements, these and other difficulties areobviated by providing devices that enable the matrix conveyor belt,which controls the speed of assembly, to be operated at a plurality ofdifferent speeds, thus permitting a proper speed of assembly to beselected according to the size of the matrices in use.

In the embodiment illustrated, the conveyor belt is operable at threediiierent speeds, namely,

(1) a high speed for use with matrices of say from 5 pt. to 14 pt.,which permits these matrices to be composed at arate ofspeed higher thannormal but still one at which the distributing mechanism can readilyhandle matrices of these sizes, (2) an intermediate speed for use withmatrices of say from pt. to 24 pt., and which is comparable to a normalspeed of composition, 5 and (3) a low speed for use with matrices of sayfrom pt. to 36 pt., which permits these matrices to be composed at anormal rate of speed as far as lines per minute is concerned, but whichlowers their speed of delivery to the assembler elevator andconsequently reduces the undesirable pounding, previously alluded to, toa degree that is acceptable. The three speeds of the conveyor belt areobtained through the medium of a gear shift mechanism operated auto- 15matically from the magazine in operative position and in a mannerdepending upon the size of matrices stored therein.

The present improvements also contemplate a star wheel operable at threediiferent speeds but in this instance there is employed a gear shiftmechanism settable manually by the operator. The speed of the star wheelwill not necessarily depend upon the speed of travel of the assembler orconveyor belt, but more upon the size of the matrices being composed andupon the size or form of the star wheel itself. In order that thematrices may be properly compacted in line in the assembler elevator, itis desirable that each matrix strikes the star wheel between twoadjacent prongs thereof, and this condition is facilitated by raising orlowering the speed of the star wheel as may be required.

In addition to the foregoing, the invention further contemplates theprovision of a clutch mechanism whereby the operator may stop theoperation of the conveyor belt and star wheel without stopping any ofthe other parts of the machine.

Referring to the drawings:

Fig. 1 is a front view of a portion of a Linotype machine equipped withthe present improvements;

Fig. 2 is aside elevation of a portionof the machine shown in Fig. l,and illustrating the devices for controlling the speed of operation ofthe conveyor belt from the magazine in operative position;

Fig. 3 is a front view of the gear shift and clutch mechanismspreviously referred to;

Fig. 4 is a horizontal sectional view taken on line dd of Fig. 3;

Fig. 5 is a front view of the clutch mechanism for connecting anddisconnecting the conveyor belt and the star wheel from the commondrive;

Fig. 6 is a sectional view on line 66 of Fig. 5;

Fig. 7 is a vertical sectional view through the gear shift mechanismcontrolling the speed of rotation of the star wheel, and showing theadjustment of the parts for driving the star wheel at the highest rateof speed;

Fig. 8 is a vertical sectional View of a part of the mechanism shown inFig. 7, with the parts set for driving the star wheel at the lowest rateof speed; and

Fig. 9 is a front elevation of the means for setting the gear shiftmechanism associated with the star wheel. 7

The matrices of the different fonts are stored in a series of magazinesA and are released therefrom under the control of a keyboard 33 which,as usual, through the medium of means including a set of escapementreeds B and escapement levers B effects the operation of the.

escapement devices B associated with the magazine located in operativeposition. As the matrices are released, they pass down or through achanneled raceway or assembler entrance C onto an inclined conveyor beltC which delivers them to the customary assembler D, wherein they areadvanced to the left and compacted as they are composed in line by arotating star wheel E, the assembler thereafter being raised as usualinto registration with the intermediate channel D through which the lineis transferred to a line transporter or first elevator (not shown) forpresentation to the mold. The magazines A are wider than usual in orderto accommodate full fonts of large matrices, say up to 36 pt.

The conveyor belt C extends at an angle transi versely of the machineand is disposed so as to receive matrices discharged from any of thechannels of the magazine in operative position. It passes (see Fig. 1)around a driven pulley C rotatably mounted on a stud fixed in the frontframe of the machine at the right and near the discharge end of themagazine and around a driving pulley C fixed to a short shaft C mountedat the left and in close proximity to the assembler elevator. The shaftC is journalled (see Fig. 4) in the front and rear plates F and F of agear box which, in addition to the shaft just mentioned, supports ashaft E on which the star wheel E is fixed as well as a shaft G on whicha driving pulley G is fixed and which serves as a common source of powerboth for driving the conveyor belt and for rotating the star wheel.

The gear box (Figs. 3 and 4), as previously stated, includes the frontand rear plates F, F secured together and heldin proper spaced relationby spacing members F and, in addition, a. third intermediate plate Fsecured to the front plate in spaced relation therewith by elements Fsimilar to the members F This intermediate plate F serves to supportsome of the parts of the gear shift mechanisms, as will be laterdescribed.

The conveyor belt driving pulley C and the star wheel E (see Figs. 3 and4) are arranged to be driven from a gear G associated with the shaft Gon which the main drive pulley G is mounted and which is arranged to bedriven from said pulley through a clutch mechanism described below. Thedrive from the gear G to the star wheel and to the conveyor belt drivepulley is through mechanism which includes in part, a wide intermediatepinion gear I-I meshing with the gear G and also with another gear Jsplined to" a sleeve J arranged to idle on a reduced portionof the shaftC on which the conveyor belt drive pulley is mounted. Likewise splinedto this sleeve are two other gears J and J all three of said gearsvarying in size, the gear J meshing with the pinion H being the largestand the other two progressively smaller.

Motion is transmitted from the gears J J and J to the star wheel E andthe conveyor belt pulley C through two independent sets of complementarygears, one set (including gears K K and K meshing, respectively, withthe gears J J and J being mounted on a short foreand-aft shaft Ljournalled in the rear and the intermediate plates F and F and whichserves to drive the star wheel, and the other set (in-- cluding gears MM and M also meshing respectively, with the gears J J and J on a similarshaft N likewise journalled in said plates and which serves to drive theconveyor belt drive pulley. The shafts L and N on which the differentsets of gears are mounted are arranged for limited fore-and-aft movementand, depending upon their setting, one or another of the gears thereonwill be operatively coupled therewith, while the two remaining gearswill merely idle thereon.

The gears K K and K are operatively coupled with the fore-and-aft shaftL (see Figs. 4, 7, and 8) through the medium of a pawl L pivotallymounted in a longitudinal recess L formed in the shaft and having a headportion Z which is urged by a spring L acting on the base of the pawl,into one or another recess K in the nature of a keyway with which eachof the gears is equipped. Of course, it will be understood that eachgear K K K rotates at a different speed, the shaft L itself consequentlyrotating at the speed of the gear which happens to be operativelycoupled with it.

The shaft L is selectively coupled with a selected gear K K or K merelyby shifting the shaft longitudinally until the head portion Z of thepawl alines with the selected gear, and when such gear is turned tobring the recess K therein in registry with the pawl, the latter will,under the action of the spring L enter the recess,

whereupon the shaft L will pick up the speed of rotation of the selectedgear.

t will be noted that the head portion Z of the pawl is formed withoppositely inclined bevelled edges, this arrangement allowing the shaftto be shifted while the parts are in motion, for as the shaft is movedlongitudinally in either direction to aline the pawl with an adjacentgear, such gear will engage one or the other of the bevelled edges ofthe pawl (depending upon the direction in which the shaft is moved),camming the same downwardly against the action of the spring L into therecess L in the shaft, in which position the pawl will remain until therecess K in the newly selected gear is brought into registry therewith,whereupon the pawl will engage in said recess in the manner previouslydescribed. Should it happen that the recess K in the adjacent or newlyselected gear is already in registry with the pawl, the camming actionof course, will not take place, since the pawl will enter immediatelyinto the recess.

In Fig. 7 there is illustrated a condition where the shaft L isoperatively connected with the rear gear K of the set, and as this gearis smaller than the complementary gear J meshing therewith, the speed ofrotation of the shaft L will be stepped up beyond that of the drivingsleeve J. In Fig. 8, there is illustrated a condition where the shaft Lis operatively connected with the front gear K of the set, and asthisgear is by longitudinally shifting said shaft.

L is shifted (see Figs. 3, 4, and 7) through the larger than thecomplementary gear J meshing therewith, the speed of rotation of theshaft will be stepped down below that of the driving sleeve J. When theshaft L is operatively connected with the intermediate gear K the shaftwill be driven at the samespeedas the driving sleeve J, for here thegears K and J have a unit ratio. 7

'The star wheel E (Figs. 3, 4, and '7), which is mounted at the frontend of theshaft E1, is driven from the fore-and-aft miovable shaft L,through the medium of a pair of intermeshing gears, one gear L keyed tosaid shaft, and the other gear E formed on a collar E loosely arrangedon the shaft E carrying the star wheel. The drive from the collar E tothe shaft E is through a comparatively heavy torsion spring E fastenedat one end to the collar, and anchored at the other end in the shaft.The spring E transmits the driving torque from the collar to the shaft,and at the same time acts as a shock absorber to lessen the strain onthe star wheel resulting from the impact thereon of large matricestraveling at high rates of speed.

The different speeds of rotation of the star wheel are obtained byoperatively coupling the shaft L with a selected one of the gears K K orK and this, as previously stated, is effected The shaft medium of an armL secured at the upper end of a short vertical shaft L journalled in anoffset portion of the front plate F and bifurcated at its free end whereit is provided with opposed inwardly extending pins 1 engaging in anannular recess Z formed in the front end of the fore-and-aft shaft. Atits lower end, the vertical shaft has fixed thereto, a forwardlyextending arm L formed with a series of bevelled teeth, meshing with abevelled gear L fixed at the rear end of a short fore-and-aft shaft Ljournalled in the front plate. Pinned at the front end of the shaft L isa handle L for effecting the manual adjustment of the parts, thearrangement being n such that as the handle is moved in a clockwisedirection,the shaftLthroughtheparts just described, will be actuatedoutwardly, whereas when thehandle is moved in the opposite directionsaid shaft will be actuated inwardly. Since there are three differentpositions for the shaft L, there are three corresponding positions ofthe handle L and these positions (see Fig. 9) are indicated by a pointerL fixed to the handle, and an associated face plate L fixed to the frontmember F of the gear box and on which there is marked opposite the threedifferent positions of the pointer, indicia representing the speeds ofrotation in revolutions per minute of the star wheel for thecorresponding settings of the shaft L. The different settings of thehandle are maintained by a spring pressed detent Z arranged in the frontplate (see Figs. '7 and 8) and adapted to engage in one or another of aseries of three recesses 1 formedin the inner face of the handle inpositions corresponding to the different settings thereof.

Theshaft N on which the gears M M and M through which the variousdriving speeds are transmitted to the conveyor belt pulley, is in allrespects similar to the shaft L on which the gears K K and K fortransmitting the variable speeds to the star wheel, are mounted. Thatis, it is journalled in the rear and intermediate plates F and F3 of thegear box and is arranged for limited fore-and-aft movement to effectoperative coupling with the different gears The various speeds of to theconveyor belt pulley (3 through a gear 'N splined on said shaft andanother gear N meshing therewith and formed on a collar N pinned on thepulley shaft C In the embodiment described, the fore-and-aft shifting ofthe shaft N to bring about operative coupling with the different gears MM and M is effected automatically and controlled from. themagazine Alocated in operative position, i. e., in registry with the assemblerentrance C. To this end (see Figs. 2 and 3) there is provided avertically disposed gear shift arm N pinned at its lower end to ahorizontal rock shaft N journalled in lugs projecting from the rear faceof the front plate F and bifurcated at its upper end where it engages inan annular groove .12 formed near the front end of the shaft N. Alsosecured to the rock shaft is a short arm N extending rearwardly andwhich is connected with a forwardly extending arm N of a bell cranklever fulcrumed on a bracket plate 13 secured to a stationary part ofthe machine in the vicinity of the magazines A. The connection justalluded' to is, through the medium of a long link N pivotally connectedat its upper end with the arm N of the bell crank lever and similarlyconnected at its lower end with the arm N. The arrangement is such that,as the bell crank lever is rocked counterclockwise (looking at themachine from the left), the horizontal rock shaft N will be turnedclockwise to shift the shaft N outwardly, whereas when the bell cranklever is rockedclockwise, the shaft will be shifted inwardy.

The bell crank lever (see Fig. 2) is turned clockwise through the mediumof a spring N fastened at one end to the link N and anchored at itsopposite end by a pin 11 fixed in the gear box frame, andcounterclockwise against the tension of said spring by cams N located oncertain of the magazines. As in the case of the shaft L associated withthe star wheel, the shaft N has three different positions of adjustment,the

rear or innermost position (which incidentally is determined by thebanking of the arm N against a banking screw n threaded in the gear boxframe) for stepping up the speed of rotation of the conveyor beltpulley, an intermediate position wherein a normal speed of rotation forthe pulley results, and an outermost or front position for stepping downthe speed of rotation of the pulley and consequently providing a speedof travel for the belt that is slower than normal.

It will now be apparent how the proper speed of travel of the conveyorbelt for matrices of a given size is selected. Let it be assumed thatthe matrices in one of the magazines are of comparatively small size, asfor instance from 5 pt.

to 14 pt., which may if the operator so desires be composed at speedsgreater than normal. In

. such case, the magazine containing these matrices will be devoid ofcams N and, when such magazine is in operative position, the shaft Nwill be located in its innermost position and the conveyor belt C thuswill have its highest speed of travel. For matrices say of 18 pt. size,the magazine wherein they are stored will be equipped with a cam Nwhich, in the operative position of the magazine, will cooperate with acam r 5 follower N located at the end of an arm N of the bell cranklever, and the throw of said cam will be such as to locate the lever inthe intermediate position, wherein the intermediate set of gears will beoperatively coupled with the shaft N, with the result that the conveyorbelt will travel at the normal rate of speed. For matrices of largersize, as for instance 36 pt., the magazine for them will be equippedwith a cam N which, in the operative position of the magazine, willlikewise cooperate with the bell crank lever, and the throw of said camwill be such as'to locate the bell crank lever so that the shaft N willbe adjusted to its outermost position wherein the gear M having the stepdown ratio with the gear J will be operatively coupled with said shaft-For this adjustment, the conveyor belt will have its slowest speed oftravel.

The various adjustments just alluded to are eifected automatically asthe different magazines are moved into operative position and, since theshaft N is in all respects similar to that controlling the speed ofrotation of the star wheel, they may be made without stopping theoperation of the parts.

The pulley G (see Fig. 1), associated with the gear box, is driven fromthe intermediate shaft through a belt and pulley,O arrangement of theusual construction. In some instances, it may be desirable to stop theoperation of the star wheel and conveyer belt without stopping theoperation of the machine, and for this purpose there is interposedbetween the pulley G and the gear G that effects the driving of thepinion H, a clutch device, which will now be described.

As shown in Figs. 3, 4, and 5, the pulley G is splined to the shaft sothat the latter is constantly driven by the pulley. Likewise splined tosaid shaft is a sleeve G on the front end of which there is formed atoothed ratchet wheel G Encircling the shaft, and mounted on spacedcollar bearings G so as to be movable relatively to said shaft, is amember G which at one end presents two spaced circular flange portions Gand G joined together by a semi-circular rib member G that encircles thetoothed ratchet wheel G3 for a portion of its peripheral edge, leavingthe remainder thereof exposed. The gear G is screwed to the front faceof the foremost flange G while between the flanges in the vicinity ofthe exposed portion of the ratchet is a dog G pivoted at its center tosaid flanges and having one end thereof pressed into engagement with theratchet wheel by a leaf spring G secured to the outer face of the ribportion G At the opposite end of the dog, there is provided a roll Garranged to track along the inner semicircumferential edge of arelatively large flat hook-shaped member P pivotally mounted at one endon the shaft C and adjacent the inner face of the rear plate F of thegear box. The member just alluded to has two positions of adjustment;one as shown in Fig. 5, wherein the dog G is held in engagement with theratchet wheel, and the other as shown in Fig. 3, wherein the dog isforced by the member P and against the tension of the spring G out ofengagement with the ratchet wheel. When the ratchet and dog are inengagement, it is apparent that the flange member G and consequently thegear G2 and the parts driven thereby (the conveyer belt and the starwheel) will be driven, whereas when the dog and ratchet wheel aredisengaged, the driving connection will be broken.

The different adjusted positions of the member P (see Figs. 5 and 6) arecontrolled by a handle P fixed. at the front end of a shaft P journalledin the front and rear plates of the gear box, and which is provided atits rear end with a cam P arranged to cooperate with a flange P struckup at the free end of the member P. Associated with the handle is aplate P formed on a sleeve P surrounding the shaft, and spaced from thefront plate F so as to clear the conveyer belt, and on which there aremarked two indications On and Off. When the handle is opposite theindication On (see Fig. 5), the low part of the cam P will engage theflange P and the member P will be located in the position wherein thedog G is operatively coupled with the ratchet wheel G whereas when thehandle is turned opposite the indication Off, the high portion of thecam will engage the flange, forcing the member P upwardly into aposition wherein it will effect the disengagement of the dog and ratchetwheel. The plate P is provided with small protrusions p which cooperatewith the handle to determine the different positions of adjustmentthereof. It might be stated that the flanges G and G are recessed as atG to provide clearance for the roll G From the foregoing, it will beapparent that the improvements referred to impart great versatilitytothe machine as far as varying the speed of assembly is concerned. Withthe mechanism. disclosed actually nine different speed combinationsbetween the assembler belt and the star wheel are available and, ifdesired, more could be obtained by increasing the number of gears in thegear box. Especially advantageous are the present improvements in viewof the trend toward wider magazines wherein matrices varying widely insize may be employed. Particularly is this true where the wide magazinesare made interchangeable with the present magazines of normal width.Then too, where matrices vary greatly in width it may be advantageous toemploy star wheels differing in design and which may require differentspeeds of rotation properly to assemble the matrices in line. These andmany other advantages are inherent in the structure herein disclosed, afew only of which are given by way of example.

In the accompanying drawings, the invention has been shown merely by wayof example and in preferred form, and obviously many variations andmodifications may be made therein which will still be comprised withinits spirit. It is to be understood, therefore, that the invention is notlimited to any specific form or embodiment,

except insofar as such limitations are specified in the appended claims.

Having thus described my invention, what I claim is:

1. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, stacker mechanism operable at different speeds foradvancing the matrices and compacting them in the assembler as the lineis being composed, and means adapted upon actuation to effect aninstantaneous change from one speed to another as required.

2. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, a rotatable star wheel arranged to advance thematrices andcompact them in the assembler as the line is being composed,a variable speed drive for the star wheel, and means adapted uponactuation to set the drive for one speed or another as required.

3. Anassembling mechanism for typographical composing machinesincluding, in combination,

an assembler wherein the matrices are composed in line, a rotatable starwheel arranged to advance the matrices and compact them in the assembleras the line is being composed, means for rotating said star wheel at aplurality of different predetermined speeds, and means for selecting onespeed of rotation or another as desired.

4. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, a rotatable star wheel arranged to advance thematrices and compact them in the assembler as the line is beingcomposed, means including a plurality of gears operable independentlyfor driving the star wheel at different speeds, and a gear shiftmechanism for rendering one or another of the gears active as desired.

5. A combination according to claim 2, wherein the speed of rotation ofthe star wheel may be varied without arresting its rotation.

6. A combination according to claim 4, wherein the gear shift mechanismis manually operable from the front of the machine.

7. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, a rotatable star wheel arranged to advance thematrices and compact them in the assembler as the line is beingcomposed, a plurality of driving gears, a plurality of driven gearsmeshing therewith, a driven shaft associated with the star wheel andwhereon the driven gears are idly mounted, and means for efiecting adriving engagement between the driven shaft and a selected one of thedriven gears, whereby to vary the speed of rotation of the star wheel.

8. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, conveyor mechanism for delivering the matrices to theassembler, means associated with the conveyor mechanism for varying therate of travel of the matrices to the assembler, and means adapted uponactuation to effect an instantaneous change from one rate of travel toanother as required.

9. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, a power driven conveyor belt for delivering thematrices to the assembler, a variable speed drive for the belt, andmeans adapted upon actuation to set the drive for one speed or anotheras required.

10. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, a power driven conveyor belt for delivering thematrices to the assembler, means for driving the conveyor belt at aplurality of diiferent predetermined speeds, .and means for selectingone speed or another as desired.

11. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, a power driven conveyor belt for delivering thematrices to the assembler, means including a plurality of gears operableindependently for driving the belt at difierent speeds, and a gear shiftmechanism for selectively rendering one or another of" the gears active.

12. A combination according to. claim 9, wherein the speed of travel ofthe conveyor belt may be varied without arresting its travel.

13. A combination according to claim 11, wherein the gear shiftmechanism is operated automatically.

14. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, a power driven conveyor belt for delivering thematrices to the assembler, a plurality of driving gears, a plurality ofdriven gears meshing therewith, a driven shaft associated with theconveyor belt and whereon the driven gears are idly mounted, and meansfor efiecting a driving engagement between the driven shaft and aselected one of the driven gears, whereby the speed of travel of theconveyor belt may be varied.

15. A typographical composing machine including, in combination, aplurality of magazines for storing matrices, means for releasingmatrices from a selected magazine, an assembler wherein the matrices arecomposed in line, a power driven conveyor belt for delivering thematrices to the as sembler, and means for varying the speed of travel ofthe belt according to the magazine selected.

16. An assembling mechanism for graphical composing machines including,in combination, an assembler wherein the matrices are composed in line,a power driven conveyor belt for delivering the matrices to theassembler and means for automatically controlling the speed of travel ofthe conveyor belt according to the size of the matrices in use.

17. A typographical composing machine adapted to be equipped withmagazines for storingmatrices of different sizes, an assembler whereinmatrices from the magazine in use are composed in line, a power drivenconveyor belt for delivering the matrices to the assembler, and meansfor varying the speed of travel of the conveyor belt according to themagazine in use, automatically as said magazine is moved into operativeposition.

18. A typographical composing machine including, in combination, aplurality of magazines for storing matrices, means for moving a selectedmagazine into operative position, means for releasing matrices from theselected magazine, an assembler wherein the matrices are composed inline, a power driven conveyor belt for delivering the matrices to theassembler, and means for varying the speed of travel of the beltautomatically as one or another of the magazines is moved into operativeposition.

typo- 19. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, a power driven conveyor belt for delivering thematrices to the assembler, a rotatable star wheel arranged to advancethe matrices and compact them in the assembler as the line is beingcomposed, a common drive for the belt and star wheel, and intermediateconnections for varying the speed of the driven members.

20. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, and means for effecting the delivery of matrices tothe assembler at different speeds.

21. An assembling mechanism for typographical composing machinesincluding, in combination, an assembler wherein the matrices arecomposed in line, means for effecting the delivery of matrices to theassembler at different speeds, and means for automatically selecting thespeed of delivery in accordance with the size of matrices in use.

22. A clutch mechanism including, in combination, a driving member, adriven member, a ratchet wheel fixed to the driving member, a

